Pointer for multiple size work blanks

ABSTRACT

A machine having a frame and a modular stack of interchangeable rotary dials mounted on the frame for carrying headed work blanks of varying shank length and diameter, fluid actuated head and shank pusher assemblies effecting compressive engagement of the work blanks against the dials when each work blank is positioned in power operated die means for a pointing operation, and a fluid circuit including adjustable air spring means providing a continuous fluid bias for actuating the head pusher and shank pusher assemblies.

United States Patent [191 Morton et a1.

[ Jan. 22, 1974 1 POINTER FOR MULTIPLE SIZE WORK BLANKS [75] Inventors: Robert D. Morton, West Hartford;

Edward G. Grohoski, Litchfield, both of Conn.

[73] Assignee: The Hartford Special Machinery Company, Simsbury, Conn.

[22] Filed: Aug. 5, 1971 [21] Appl. No.: 169,207

[52] U.S. Cl 10/169, 10/9, 10/21 [51] Int. Cl..... B2lk 27/00, B23g 9/00, 823g 11/00 [58] Field of Search 10/4, 6, 9,19, 20.5, 21, 23, 10/39, 68, 69, 52, 60, 69, 158, 169, DIG. 2,

DIG. 3; 269/32, 57

[56] References Cited UNITED STATES PATENTS 1,546,914 7/1925 Calkins lO/39 X 1,184,033 5/1916 Scofield....

3,111,697 11/1963 Wilson 3,252,367 5/1966 Nann 2,415,037 l/l947 Redrner 3,289,228 12/1966 Lofgren et a1. 10/6 2,335,258 11/1943 Butler lO/19 1,166,621 l/l9l6 Monks 2,674,754 4/1954 I'Iale 3,435,472 4/1969 Haines 10/169 FOREIGN PATENTS OR APPLICATIONS 1,003,169 0/1957 Germany 1. 10/21 Primary Examiner-Richard J. Herbst Assistant Examiner-E. M. Combs Attorney, Agent, or Firm-Prutzman, Hayes, Kalb &

Chilton [5 7 ABSTRACT A machine having a frame and a modular stack of interchangeable rotary dials mounted on the frame for carrying headed work blanks of varying shank length and diameter, fluid actuated head and shank pusher assemblies effecting compressive engagement of the work blanks against the dials when each work blank is positioned in power operated die means for a pointing operation, and a fluid circuit including adjustable air spring means providing a continuous fluid bias for actuating the head pusher and shank pusher assemblies.

11 Claims, 5 Drawing Figures POINTER FOR MULTIPLE SIZE WORK BLANIKS This invention generally relates to work blank forming machines and particularly concerns point formers for pointing multiple size headed work blanks.

BACKGROUND OF THE INVENTION Recent demands have produced stringent requirements for high quality, premium priced specialty pointed fasteners of a type which not only are selftapping but are also self-drilling in addition to providing the normal fastening function. To produce these specialty fasteners, such as drill point or self-drilling screws, for example, their shanks must normally be pointed before being rolled, and it is imperative to provide exceptionally reliable pointing control to precisely locate each work blank relative to the pointing dies. During a high speed production operation, nearly ideal control of the blank during its transfer to and positioning within the dies is required, particularly when the desired operating speed on an automatic point former machine is about 600 to 700 pieces per minute. Additional problems such as variations in inertia of the operating components, frictional drag and the like are normally encountered in adapting such machines to accommodate work blanks of varying shank length and diameter.

OBJECTS OF THE INVENTION Accordingly, a primary object of this invention is to provide a new and improved machine for effecting point forming operations on work blanks and which provides significantly improved alignment, retention and control of each work blank during a high speed production operation to provide high quality fasteners.

Another object of this invention is to provide an improved machine of the type described which is quick and easy to set up and adjust for work blanks of different size at a desired machine operating speed.

A further object of this invention is to provide such an improved machine having a rotary dial-type index ing mechanism particularly suited for facile modification to accommodate work blanks of different size.

Still another object of this invention is to provide such an improved machine having adjustable, fluid actuated aligning and retaining devices for precisely positioning each work blank. Included in this object is the aim of providing such a device of composite construction requiring a minimum number of parts to accommodate a full range of blank lengths and having work engaging portions which are quick and easy to replace in an economical manner.

Other objects will be in part obvious and in part pointed out in more detail hereinafter.

A better understanding of the objects, advantages, features, properties and relationships of the invention will be obtained from the following detailed description and accompanying drawings which set forth certain il- Iustrative embodiments and are indicative of the ways in which the principle of the invention is employed.

In the drawings:

FIG. 1 is a partial perspective view of a machine incorporating this invention;

FIG. 2 is an enlarged side view, partly broken away and partly in section, of part of a point forming station of the machine of FIG. 1 and showing an arrangement of stacked index plates for accommodating a work blank of preselected size;

FIG. 3 is an enlarged side view, partly broken away and partly in section, showing another arrangement of stacked index plates for accommodating a work blank of a size different from that of FIG. 2;

F IG. 4 is a sectional view, partly broken away, taken generally along line 44 of FIG. 2; and

FIG. 5 is a sectional view, partly broken away, taken generally along line 5-5 of FIG. 2.

Referring to the drawings in detail, a machine incorporating a preferred embodiment of this invention is shown having a vibratory hopper 12 mounted on a frame 14. Headed work blanks are fed from the hopper 12 under a clearing wheel 16 into an inclined gravity feed track 18. The clearing wheel 16 is adjustable for ensuring that a head of each blank such as at 20 is properly positioned in the feed track 18. The slot width and height of the feed track 18 may be adjusted in accordance with varying blank sizes by suitable screw adjustment devices such as at 22 and 24, and a main feed cover 26 and extension cover 28, which is pivotally supported for swinging movement about a horizontal axis at a lower end portion of the main cover 26, ensure work blank guidance and free and easy transfer of blanks from the feed track 18 to a rotary dial-type work blank transferring and positioning mechanism or indexing mechanism 30.

As fully explained in US. Pat. application Ser. No. 149,520 to Robert D. Morton filed June 3, 1971, assigned to the assignee of this invention and entitled Combination Point Former and Thread Roller Machine, a motor-driven variable feed drive, not shown, power operates a connecting rod 32 to drive a ball joint 34 pivotally secured to a slide 36 mounted within suitable bearings 35% on the frame 14. Reciprocation of the slide 36 drives a movable die housing 40 along a path of movement perpendicular to that of the blanks 20 in the feed track 18 and toward and away from a fixed die housing 42 secured to a mounting block 44 attached to the frame 14. An appropriate set of dies 46, 48 are installed in the housings 40, 42 in precise orientation to the indexing mechanism 30 to ensure that the dies 46, 48 will precisely register with a shank 50 of a blank 20 extending between the dies 46, 48 from the indexing mechanism 30 such that the shank tip of each work blank may be pointed in a forging-type operation produced by a single forging blow each time the slide 36 moves from right to left (as illustrated in FIGS. 1 and 2) to its extreme limit position.

The indexing mechanism 30 is mounted on a generally L-shaped frame member 52 (FIG. 2) supported on a base 54. The base 54 is supported for swinging movement toward and away from the feed track 18 about a horizontal pivot shaft 56 secured to the mounting block 44. As fully described in the above referenced patent application, the height of the frame member 52 relative to the dies 46, 48 is readily adjusted by a handle 58 on a suitable lead screw 60. The lead screw 60 is threadably connected to the frame member 52 whereby the indexing mechanism 30 may be precisely adjusted relative to the pointer dies 46, 48 in accordance with a predetermined shank length of the blank to be pointed.

As the column of blanks are fed from a track end 62 at a so-called 12 oclock position relative to the indexing mechanism 30 (FIG. 1), the blanks are sequentially indexed a quarter turn counterclockwise into a 9 oclock position between the dies 46, 48. Thereafter, pointed blanks are delivered to a discharge bin 64 or other suitable outlet which is preferably located downstream of the pointing station in a 6 oclock position.

Such indexing movement is effected by an advance pawl 66 which operates a ratchet 68 supported on top of the frame member 52 in coaxial driving relation to a dial assembly 76 of the indexing mechanism 36. The advance pawl 66 is driven by an index actuating piston 72 supported for longitudinal reciprocation in an operating cylinder 74 formed in the frame member 52. A. driving connection between the piston 72 and the advance pawl 66 is provided by a connecting pin 76 extending upwardly through a slot 78 in the frame member 52.

Operation of the slide 36 moves the movable die housing 40 and an operating lever 86, carried by the housing 46, from right to left as viewed in FIG. 1 to effeet a point forming operation during which time a noback pawl 82 maintains the ratchet 68 and dial assembly '70 in a fixed position. Upon return movement to the right of the piston 72, the connecting pin '76 operates the advance pawl 66 to drive the ratchet 68 counterclockwise and advance the dial assembly 70 through a preselected incremental angular displacement. Dial movement simultaneously effects receipt of a fresh work blank 26 in a 12 oclock position from the track end 62 of the feed track 118 and positions a work blank carried by the dial assembly 76 into a 9 oclock position between the pointer dies 46., 418 while discharging a pointed blank in a 6 oclock position into the discharge bin 64%.

To offer optimum accommodation of blanks of different shank length and diameter, a modular stacked index plate arrangement is provided for tooling economy and reduction of dial assembly inertia, particularly during handling of blanks of relatively long shank length. FIG. 2 shows an arrangement according to this invention wherein two spaced apart concentric dials 84 and 86 are secured by suitable fasteners (only one shown-at 88) in assembled coaxial relation to a dial housing 90 and the ratchet 68. This entire dial assembly 70 is supported on the frame 52 for synchronous rotation in response to an indexing movement effected by the advance pawl 66. The dials 84, 86 are shown fixed on opposite axial end surfaces of a spacer plate 92 with the upper dial 84 being shown interposed between spacer plate 92 and second spacer plate 94 secured on the bottom of the dial housing 96 with each dial and spacer plate being tailored for a specific assortment of blank diameter and blank length sizes. Peripheral portions of the dials 84 and 86, positioned approximately along the angular path of blank movement between the 12 oclock and 6 oclock positions, are respectively enclosed by a pair of retaining plates 96 and 98 shown in FIG. 2 suitably secured in fixed relation to the frame member 52 in generally coplanar relation to the dials 84 and 86. The retaining plates 96, 98 each have arcuate inner peripheral edge surfaces (such as shown at 100 on plate 96 in FIG. 4) in radially outwardly disposed adjacent relation to the periphery of their respective dials 84, 86 for maintaining continuous control over each work blank as it is indexed through the diametrically opposed entrance and exit positions in the pointing station. A similar arrangement of spacer elements 162 and 1164 are provided for positioning the retaining plates 96 and 98 with the spacer elements 102, 104 being fixed to the frame member 52. In FIG. 3 only one spacer element 162 and only one retaining plate 96' is provided for a pair of dials 86, 86' utilized to accommodate a blank 26' of reduced shank length in comparison to that of the blank 26 shown in FIG. 2. Radially outwardly facing work blank engagement grooves 166, 168 and 166', 168' are provided at equiangularly spaced locations about the periphery of each dial 8 3, $6 and 84', 36 with the grooves in each dial being correspondingly circumferentially spaced to extend parallel to the central axis of each dial.

A set of dial modules of varying diameter grooves and thicknesses accordingly may be provided to accommodate a full range of blanks to be pointed, and dials of different thicknesses with work blank engagement grooves of the same size are readily interchangeable for modifying the point former to accommodate a full range of work blank shank lengths for a given diameter size.

As a result of changes in dial plate buildup and variations in operating speeds of a machine, the inertia of a given indexing mechanism will vary from one production operation to the next depending on the size blanks to be pointed. In addition, frictional drag of an indexing mechanism on its bearing assembly normally varies from one machine to another. To conveniently customize the dial indexing action for a variety of multiple size blanks at varying operating speeds in different machines, an air spring is incorporated in the frame member 52 to serve not only as an air cushion upon actuation of the indexing piston 72, but also to effect a controlled return of the piston 72 from left to right during an indexing movement upon retraction of the slide 36. For this purpose the operating cylinder 74 is provided with an inlet orifice llltl shown formed in end plate 112. Orifice H6 is in constant communication via a conventional fluid supply line 114 to a source of pressurized fluid such as compressed air to continuously pressurize the one end of the cylinder 74 adjacent end plate 112 to power return piston 72 toward the right under motive fluid pressure for operating the indexing mechanism 30 while also providing an impact absorbing fluid cushion between end plate 112 of the operat ing cylinder 74 and the piston '72 during its power stroke in the opposite linear direction. A suitable O- ring seal 116 is shown circumferentially extending about the outer diameter of piston 72 to minimize undesired leakage of air past the piston 72 within the cylinder 74. Operation of the indexing mechanism 30 may be conveniently stopped upon manual actuation of a lever operated locking block 118 pivotally supported on the frame member 52 for engagement within a locking groove 126 in the operating piston 72.

To tailor the pressure force within the cylinder 74 to closely correspond to an optimum force required for a preselected speed of operation in accordance with the weight of the assembled component parts of the dial assembly 76 and work blank size of a particular job, a conventional air pressure regulator I22 is shown in the supply line 1 l4. Adjustment of the pressure of the compressed air within the cylinder 74 to a predetermined level accordingly may be set for a broad range of performance requirements for a variety of work blank sizes in a single machine.

To further ensure ideal control over each blank during its tranfer and positioning within the pointing station between the dies 46, 48, an adjustable head pusher assembly 124 (FIG. 5) is provided to effect a variable force on a button 126 provided on a lower terminal end of a plunger 128 reciprocably mounted in an opening 130 in the frame member 52. Opening 1311 extends generally perpendicular to the dial @4- at approximately the 9 oclock position immediately above the pointer dies 46, 48. The opening 130 constitutes termination of an air supply passageway 132 which may be connected to a source of compressed air through tubing 1353. An enlarged lower portion of the opening 130 is fitted with a suitable bearing cup 134 and O-ring seal 136 providing a fluid-tight sealing arrangement for receiving a relatively enlarged lower diameter portion of the plunger 128. The plunger 128 has an upper stern of relatively reduced diameter projecting through a central opening 138 of relatively enlarged size in an adjustment sleeve 140 threadably secured in the frame member 52 within the opening 130. The juncture of the double diameter portions on the plunger 128 provides a pressure surface shoulder 142 normally subjected to a downwardly directed force due to fluid pressure within the passageway 132. An annular spacer 144 is normally bottomed on an exposed manual adjustment knob portion 146 of the sleeve 140 and retained in position by a retaining ring 148 fitted within a circumferentially extending groove 150 on an outwardly projecting portion of the plunger stem to establish a lower limit position for the plunger 128. This construction permits the plunger 128 to be cammed upwardly relative to the sleeve 1411 upon movement of headed portions of the work blanks under the plunger 128 and into the pointing station between the dies 46, 48. Manual rotation of sleeve 140 accordingly provides preselected height adjustment relative to the frame member 52 and varies the lower limit position of the plunger 128 to accommodate work blanks of varying head sizes and styles. Sleeve 146 is preferably maintained in a selected position to establish the predetermined lower limit position of plunger 128 by means of a suitable detent such as at 152 shown urged radially inwardly against an outer threaded portion of sleeve 140 by a spring 154. The resilient bias of the spring 154 is shown selectively set by a pair of set screws 156 threadably received within a threaded opening 158 in frame member 52.

The height adjustment knob portion 146 of sleeve 140 accordingly provides convenient positioning of the head pusher button 126 to accommodate varying head heights of work blanks without sacrificing the capability of the assembly to seat varying styles of heads against the upper surface of the upper dial 64. The button 126 preferably has a chamfered peripheral shoulder 160 which serves to engage each work blank head despite contour variations as it enters its 9 oclock position between the pointing dies 46, 48 to firmly apply a force axially of the blank and compressively seat its head on the upper dial surface and provide accurate control of the attitude of the work blank shank and the height of its tip relative to the dies 46, 46 for the point forming operation. The force applied is adjustable for accommodating multiple size blanks by a conventional air pressure regulator 162 in the tubing 133.

Radial control of each work blank is controlled by a shank pusher assembly 164 which applies a radially inwardly directed force to each blank at a height corresponding to that of the dials 84 and 86 to'provide precision location of each work blank shank by compressively engaging it against the dials 64, 86 within their respective grooves 106, 108 as each blank passes into its 9 oclock position for the pointing operation. the embodiments shown in FIGS. 2 and 3 respectively illustrate a pair of shank pusher assemblies 164, 164 for a relatively long work blank 26 and a single shank pusher assembly 164 for precision location of a relatively short work blank 20'. For simplicity of description, the shank pusher assembly 164 for dial 84 will be described as it will be understood that each assembly is substantially identical in construction and function. A shank pusher lever or leg 166 is supported for swinging move ment on an upper surface of its respective retaining plate 96 about a generally vertical pivot shaft 168 fixed relative to the frame member 52. The retaining plate 96 is shown with suitable cutout portions 1711 for receiving a work blank engagement foot 172 on the leg 166 of each shank pusher assembly 164. The foot 172 of each of the shank pushers illustrated in FIG. 2 are identical although the foot 17 2' shown in FIG. 3 is provided with an'enlarged depending work blank engagement surface which may be economically utilized to provide the above-described compressive engagement of the shank 211' against both of the stacked dials 84', 86' without necessitating a separate shank pusher assembly for each dial due to the reduced axial length of the work blank shank. It will be appreciated that an assortment of only three feet portions, two of which are identical, will accommodate a full range of blank lengths. Moreover, each of the shank pusher feet 172 are preferably secured by removable fasteners such as the illustrated machine screws 174 in FIG. 4 which secure the foot 172 to its leg 166 and additionally provide economical, facile replacement of that portion of each shank pusher assembly subjected to maximum wear.

The leg 166 of each shank pusher assembly 164 is adjustably biased under the influence of an air actuated plunger 176 having one end portion drivingly engaging the leg 166 and an opposite end portion continuously received within a bushing 1711 fitted within a terminal outlet of a fluid passageway shown drilled in the frame member 52 and continuously exposed to compressed air directed into the passageway 180 via a fluid coupling 182 and conduit 184 leading a source of compressed air. Accordingly, the shank pusher foot 172 of each assembly 164 is continuously urged radially inwardly against a work blank positioned between the dies in the pointing station. To effect a desired force pattern to precisely position each blank within the pointing station, an individual air passageway 180 and individual pressure regulator 186 is provided for each air passageway so that each shank pusher assembly 164 may be adjusted independently.

To maintain adjacent surface areas clean and free of metal chips resulting from the pointing operation and to further ensure a quality production operation under high speed operating conditions, a preselected clearance is preferably provided between the plunger 176 and its bushing 178 to permit air to vent around the plunger 176 and effect chip clearance at the pointing station.

A machine of the above-described type has been found to work satisfactorily under relatively high speeds, that is, up to between 600 and 700 pieces per minute, and yet produce precisely formed specialty fasteners. Ideal control of the blank transferring and positioning within the pointing station is achieved by virtue of the disclosed work blank aligning and retaining means provided by the disclosed head pusher and shank pusher assemblies to effect continuous axial and radial control of the work blanks relative to the dial and pointed dies. Utilization of the disclosed modular stacked index plates for optimum accommodation of any work blank length of given shank diameter further ensures precision orientation of each work blank within the pointing station.

As will be apparent to persons skilled in the art, various modifications, adaptations and variations of the foregoing specific disclosure can be made without departing from the teachings of the present invention.

What we claim is:

l. A point former machine for pointing multiple size shanks of headed work blanks and comprising a frame, a point forming station including power operated die means operably mounted on the frame, means for feeding work blanks to the point forming station, a work blank transferring and positioning mechanism for automatically receiving and transferring blanks from the feeding means into position in the point forming station for a pointing operation, the transferring and positioning mechanism including a modular index assembly which is interchangeable with other modular index assemblies to accommodate work blanks of various shank lengths and diameters, the index assembly including a module of co-axially stacked dials supported for synchronous rotation on the frame and having correspondingly circumferentially spaced work blank engagement grooves, fluid circuit means mounted on the frame and defining first and second passageways connected to a source of pressurized fluid, a first plunger mounted in the first passageway for applying a biasing force to the head of each work blank at the point forming station urging the blank axially toward the die means and into seating engagement with the index assembly, a second plunger mounted in the second passageway for applying a biasing force to the shank of each work blank at the point forming station urging the blank radially inwardly against the stacked dials of the index assembly, an individual adjustable fluid pressure regulator in each of the first and second passageways for control adjustment of the forces applied to the head and shank portions of the work blank at the point forming station to selectively tailor compressive engagement of that work blank within its work blank engagement grooves of the stacked dials in accordance with the work blank size and the operating speed of the machine, an operating cylinder mounted on the frame and having one end portion in communication with the source of pressurized fluid, and an indexing piston reciprocably mounted in the cylinder to be power driven in one direction toward said one end portion of the cylinder for conditioning the transferring and positioning mechanism for an indexing movement, the pressurized fluid in said one end portion of the chamber providing a fluid cushion upon the piston being power driven in said one direction and effecting return movement of the piston in the opposite direction for indexing the transferring and positioning mechanism for the next point forming operation.

2. A point former machine for pointing multiple size shanks of headed work blanks and comprising a frame, a point forming station including power operated die means operably mounted on the frame, means for feeding work blanks to the point forming station, a work blank transferring and positioning mechanism for automatically receiving and transferring blanks from the feeding means into position in the point forming station for a pointing operation, the transferring and positioning mechanism including a modular index assembly which is interchangeable with other modular index assemblies to accommodate work blanks of various shank lengths and diameters, the index assembly including a module of co-axially stacked dials supported for synchronous rotation on the frame and having correspondingly circumferentially spaced work blank engagement grooves, fluid circuit means mounted on the frame and defining first and second passageways connected to a source of pressurized fluid, a first plunger mounted in the first passageway for applying a biasing force to the head of each work blank at the point forming station urging the blank axially toward the die means and into seating engagement with the index assembly, a second plunger mounted in the second passageway for applying a biasing force to the shank of each work blank at the point forming station urging the blank radially inwardly against the stacked dials of the index assembly, and an individual adjustable fluid pressure regulator in each of the first and second passageways for control adjustment of the forces applied to the head and shank portions of the work blank at the point forming station to selectively tailor compressive engagement of that work blank within its work blank engagement grooves of the stacked dials in accordance with the work blank size and the operating speed of the machine, the fluid circuit means being connected to a source of compressed air, and the second plunger being of smaller size than its corresponding passageway to provide a preselected clearance for air ejection to clear adjacent surface areas of metal chips resulting from the point forming operation.

3. The machine of claim 1 further including a lever pivotally mounted on the frame for swinging movement radially of the stacked dials, and wherein the second plunger is reciprocably mounted in its passageway for drivingly engaging the lever and continuously biasing it radially inwardly toward the dials to compressively engage the shank of each blank against the dials during a point forming operation.

4. The machine of claim 3 wherein the lever includes a work blank engagement foot mounted thereon, the work blank engagement foot being removably secured to the lever for facile replacement.

5. The machine of claim 1 further including a fluid pressure regulator for varying pressurization of the cylinder as determined by a preselected operating speed of the machine and in accordance with the weight of the assembled component parts of the transferring and positioning mechanism and the size of the work blanks carried thereby.

6. The machine of claim 1 wherein the first plunger is reciprocably mounted in its passageway in overlying relation to a peripheral portion of the dial above the die means, the actuating plunger being reciprocable along an axis of movement coaxial with the shank of a work blank at the point forming station for movement toward and away from the dial, the actuating plunger being engageable with a headed portion of each blank carried by the dial into position at the point forming station to apply a pressure force axially of the work blank to firmly seat it on the dial and uniformly control the height of the shank tip relative to the die means.

7. The machine of claim 6 wherein a lower exposed end portion of the first plunger has a radially enlarged flange with a chamfered peripheral shoulder engageable with a heated portion of each work blank at the point forming station for smooth accommodation of work blank head portions of varying contour.

8. The machine of claim 6 wherein the first plunger includes a portion of reduced diameter providing a shoulder intermediate the axial length of the plunger serving as a pressure surface area, a sleeve mounted in the frame and having a central opening receiving the actuating plunger for free axial movement, stop means establishing a lower limit position for the first plunger relative to the sleeve upon the first plunger being thrust downwardly toward the dial under the fluid bias, and the sleeve being axially adjustable relative to the frame for selectively raising and lowering the height of the lower limit position of the first plunger relative to the dial for accommodating head height variations in work blanks being positioned in the point forming station.

9. The machine of claim 8 further including releasable detent means engageable with the sleeve for securing the same in a selected position relative to the frame.

10. The machine of claim 8 including a sealing subassembly mounted within the first passageway about the first plunger and providing perimeter sealing to prevent fluid leakage between the first plunger and its passageway whereby the first plunger is subjected to the pressure of a trapped volume of fluid.

11. The machine of claim 1 wherein the work blank transferring and positioning mechanism automatically transfers work blanks through an angular path of movement between a first entrance position adjacent the feeding means upstream of the die means and a second exit position, the die means being intermediate said first and second angular positions and wherein a plurality of plates corresponding in number to the dials are fixed to the frame in generally coplanar relation to the dials with an edge surface of each plate being in radially outwardly disposed adjacent relation to the periphery of its respective dial for maintaining control over each work blank radially of the dials during work blank movement between said first and second angular posi- 

1. A point former machine for pointing multiple size shanks of headed work blanks and comprising a frame, a point forming station including power operated die means operably mounted on the frame, means for feeding work blanks to the point forming station, a work blank transferring and positioning mechanism for automatically receiving and transferring blanks from the feeding means into position in the point forming station for a pointing operation, the transferring and positioning mechanism including a modular index assembly which is interchangeable with other modular index assemblies to accommodate work blanks of various shank lengths and diameters, the index assembly including a module of co-axially stacked dials supported for synchronous rotation on the frame and having correspondingly circumferentially spaced work blank engagement grooves, fluid circuit means mounted on the frame and defining first and second passageways connected to a source of pressurized fluid, a first plunger mounted in the first passageway for appLying a biasing force to the head of each work blank at the point forming station urging the blank axially toward the die means and into seating engagement with the index assembly, a second plunger mounted in the second passageway for applying a biasing force to the shank of each work blank at the point forming station urging the blank radially inwardly against the stacked dials of the index assembly, an individual adjustable fluid pressure regulator in each of the first and second passageways for control adjustment of the forces applied to the head and shank portions of the work blank at the point forming station to selectively tailor compressive engagement of that work blank within its work blank engagement grooves of the stacked dials in accordance with the work blank size and the operating speed of the machine, an operating cylinder mounted on the frame and having one end portion in communication with the source of pressurized fluid, and an indexing piston reciprocably mounted in the cylinder to be power driven in one direction toward said one end portion of the cylinder for conditioning the transferring and positioning mechanism for an indexing movement, the pressurized fluid in said one end portion of the chamber providing a fluid cushion upon the piston being power driven in said one direction and effecting return movement of the piston in the opposite direction for indexing the transferring and positioning mechanism for the next point forming operation.
 2. A point former machine for pointing multiple size shanks of headed work blanks and comprising a frame, a point forming station including power operated die means operably mounted on the frame, means for feeding work blanks to the point forming station, a work blank transferring and positioning mechanism for automatically receiving and transferring blanks from the feeding means into position in the point forming station for a pointing operation, the transferring and positioning mechanism including a modular index assembly which is interchangeable with other modular index assemblies to accommodate work blanks of various shank lengths and diameters, the index assembly including a module of co-axially stacked dials supported for synchronous rotation on the frame and having correspondingly circumferentially spaced work blank engagement grooves, fluid circuit means mounted on the frame and defining first and second passageways connected to a source of pressurized fluid, a first plunger mounted in the first passageway for applying a biasing force to the head of each work blank at the point forming station urging the blank axially toward the die means and into seating engagement with the index assembly, a second plunger mounted in the second passageway for applying a biasing force to the shank of each work blank at the point forming station urging the blank radially inwardly against the stacked dials of the index assembly, and an individual adjustable fluid pressure regulator in each of the first and second passageways for control adjustment of the forces applied to the head and shank portions of the work blank at the point forming station to selectively tailor compressive engagement of that work blank within its work blank engagement grooves of the stacked dials in accordance with the work blank size and the operating speed of the machine, the fluid circuit means being connected to a source of compressed air, and the second plunger being of smaller size than its corresponding passageway to provide a preselected clearance for air ejection to clear adjacent surface areas of metal chips resulting from the point forming operation.
 3. The machine of claim 1 further including a lever pivotally mounted on the frame for swinging movement radially of the stacked dials, and wherein the second plunger is reciprocably mounted in its passageway for drivingly engaging the lever and continuously biasing it radially inwardly toward the dials to compressively engage the shank of each blank against the dials during a point forming operation.
 4. The machine of claim 3 wherein the lever includes a work blank engagement foot mounted thereon, the work blank engagement foot being removably secured to the lever for facile replacement.
 5. The machine of claim 1 further including a fluid pressure regulator for varying pressurization of the cylinder as determined by a preselected operating speed of the machine and in accordance with the weight of the assembled component parts of the transferring and positioning mechanism and the size of the work blanks carried thereby.
 6. The machine of claim 1 wherein the first plunger is reciprocably mounted in its passageway in overlying relation to a peripheral portion of the dial above the die means, the actuating plunger being reciprocable along an axis of movement coaxial with the shank of a work blank at the point forming station for movement toward and away from the dial, the actuating plunger being engageable with a headed portion of each blank carried by the dial into position at the point forming station to apply a pressure force axially of the work blank to firmly seat it on the dial and uniformly control the height of the shank tip relative to the die means.
 7. The machine of claim 6 wherein a lower exposed end portion of the first plunger has a radially enlarged flange with a chamfered peripheral shoulder engageable with a heated portion of each work blank at the point forming station for smooth accommodation of work blank head portions of varying contour.
 8. The machine of claim 6 wherein the first plunger includes a portion of reduced diameter providing a shoulder intermediate the axial length of the plunger serving as a pressure surface area, a sleeve mounted in the frame and having a central opening receiving the actuating plunger for free axial movement, stop means establishing a lower limit position for the first plunger relative to the sleeve upon the first plunger being thrust downwardly toward the dial under the fluid bias, and the sleeve being axially adjustable relative to the frame for selectively raising and lowering the height of the lower limit position of the first plunger relative to the dial for accommodating head height variations in work blanks being positioned in the point forming station.
 9. The machine of claim 8 further including releasable detent means engageable with the sleeve for securing the same in a selected position relative to the frame.
 10. The machine of claim 8 including a sealing subassembly mounted within the first passageway about the first plunger and providing perimeter sealing to prevent fluid leakage between the first plunger and its passageway whereby the first plunger is subjected to the pressure of a trapped volume of fluid.
 11. The machine of claim 1 wherein the work blank transferring and positioning mechanism automatically transfers work blanks through an angular path of movement between a first entrance position adjacent the feeding means upstream of the die means and a second exit position, the die means being intermediate said first and second angular positions and wherein a plurality of plates corresponding in number to the dials are fixed to the frame in generally coplanar relation to the dials with an edge surface of each plate being in radially outwardly disposed adjacent relation to the periphery of its respective dial for maintaining control over each work blank radially of the dials during work blank movement between said first and second angular positions. 